Mechanical movement



Nov. 25, 1930. w. F. REscHKE MECHANICAL MOVEMENT Filed Aug. 19, 1929 2 SheetsfSheet l f nl [im INVENTOR h/f//zrzz FPesc/ve 6` f l. ATTORNEY Nov. 25, 1930. w.` F. REscHKE 1,782,697

MECHAN I CAL MOVEMENT Filed Aug. 19, 1929 2 Sheets-Sheet 2 /NVENTOR 130 the pump plunger moved down slowly Patented Nov. 25, 1930 n .A

`W'ILLIAM r. nnscnxn, or wlcni'rn. KANsAs" 1 p MECHANICAL Movnivrnnr Y Appiicaiion sied August 19, i929." seal no. 386.898.

"This invention relates toa mechanical .movementl for `translating rotary motion to reciprocatory rectilinear motion .and while it is susceptible ot multitudinous applications,` i itis particularly designed oruse in `connection with pumping apparatus for deep wells n such'as oil wells andthe like. In ordinary oilwell pumping practice, the movement of. thcifront end of the walking beam ina down "war'd 'direction is at the same speed as the p upward movement or lift andjust as soon as the plunger ot the working barrel reaches the end 'of its down-stroke, it` starts toV littl to raise the fluid throughthe tubingto the direction of movement puts considerable` strain upon the sucker rods causing them to whip and `break either by crystallization or` byparting at the joints. 'Ihe frequent shut-i downs at the well caused by the breaking of thesucker rods reduces the production atthe well with the attendant losses.

Furthermore, if the stroke of the walking `beam is such that the plunger in the Vworking barrel moves on its down-stroke too rapidly,A there is not time enough for the oil to pass the standing valves before the up-strokeror litt begins.` As a result, the efficiency ot the i pump is below that which and raisedrapidly. It is also obvious that at the beginning of the lift stroke of the walkingbeam,` the dynamicresistance or inertia of thefluid causes an appreciable increase stroke with the gearing in low and after the moment ot inertia is overcome, the gear# ing will s eed up so as to increase the speed of the li tuntil it reaches its peak at the end of the lift stroke and I have provided a mechanical movement or gearing which will `counterbalance the weight of the sucker rods and theplunger.

The gearing 1s so designed `that when the it would have it.

in the load placed upon .the prime mover so that the prime mover ormotor must `be sub-;

rods, working barrelor pump plunger are being" lowered into the well for the intake stroke `of thepump, Athe gears are lifted, p assisted, of course, by the motor. Then, onl the upstroke of" the walking beam to lift 55 the rods, the plunger and the fluid, the gears move downward, their weight `materially assistingthemotor in raising the sucker rods, pump plunger andthe fluid. "Ihis arrangement" reducestheystrain and load on `the `motorsothatv a comparatively small power 4unltwill suiiice" and the wear and -tear on the motor will be reduced to aminimumbe cause it will notlbe subjected to sudden heavy loads.` -f `1 K i Ihave alsonprovided means forvarying the "throw ofthe walkingbeam or for varying"` the points on two meshing eccentric` gears at whichthe peak of the lift-.will occur.

'Ihe novel manner of overcoming the'obj ections above enumerated will be specifically described hereinafter, reference being had to" the accompanying drawings in which:

Fig. l is a sideview of a pumping mechanism to which my invention `is applied.

Fig. 2 is a plan view ofthegearing yshown in Fig. l. i

` Fig. 3 is a diagrammatical view of the two eccentric gearsand the adjustable link bar` with which Lthey "are'associ'ated, the gears being here shown as operating anV air compressing pist'tui.v x

TFig. 4 is a` diagrammatic view of the two eccentric gears and the adjustable link bar arranged to reach the end ofthe lift stroke at about lQO-degrees ofthe-y cycle o rotation Vof! the drive gear, theegearsbeing shown atA the beginning of the up-stroke.

Fig. 5 is a similar `view showing the-gears inlposition` at theend of thefup-stroke.

Fig. 6 is a view showing the parts" arranged to reach the `peak of the .up-stroke at approximately 145 degrees of the cycle of rotation of the drive gear, the parts being shown at thebeginning of the up-stroke. 3

f Fig. 7 is a similar view showing the parts arranged as in Figure 6 after the walking beam reaches thelimit ofthe up-stroke.

Fig. 8 is a diagrammatic view showing the parts arranged to cause the walking beam to reach the limit of its up-stroke at approximately degrees of the cycle of rotation of the drive gear.

Fig. 9 .is a diagramma-tic view of the arrangement shown in Figure 8, illustrating the parts at the limit of the up-stroke and F ig. 10 is a graphic chart showing the eflieiency curves for the three sets of diagrams illustrated in Figures 4 to 9, both inclusive.

Referring now to the drawings by numerals of reference, 1 and 2 designate two sills of a frame having uprights or standards 3 and 4 in which a walking beam 5 is tulcrumed through the pivot 6. The standards 3 and 4 are braced to the sills by the diagonal braces 7 and 8 but additional braceslmay be used if desired. At the front ot the walking beam is an arcuate member 9 commonly called a mule head to which a cable 10 is secured, in turn, connected to the polish rod in the usual way.

The numeral 11 designates a prime mover or motor, the drive shaft 12 of which is mounted in a bearing 13 on the brace 7. The drive shaft 12 carries a pinion 14, meshing with a gear 15 on shaft 16 in bearings 17 and 18 carried by the braces 7 and 8. The shaft 16 carries a pinion 18 which meshes with a gear 2O on shaft 21 in bearings 22 and 23 carried by the braces 7 and 8.

Between the ends oi the shaft 21 is fixed thereto a gear 24 eecentrically mounted on the shaft and it meshes with a like gear 25, the two gears being held in mesh by a boxlike yoke consisting of the curved end bearing heads 26 and 27 against the inner faces of which the shrouds 28 and 29 ride so that the. projecting teeth of the gears 24 and 25 will be held in mesh, it being understood that the bearing heads 26 and 27 are channeled to provide for the passage of the teeth as the shrouds roll on them and it is to be further understood that the shrouds of the gears 24 and 25 roll one upon the other. The heads are connected by the adjustable tierods 30 and 31 which pass through the heads 26 and 27 and are provided with'adjusting nuts 32 and 33. Eccentrically mounted on opposite faces of the gear 25 are cross-heads 34 and 35 which are connected to the walkin g beam and the reins 36 and 37. The reins engage a cross-pin 38 carried by the bearing 39 on the walking beam (see Figure 1).

By reference to Figure 1 it will be seen that I have provided vertically and laterally adjustable links 4() and 41 which have holes 42 at their inner ends adapted to be adjustably connected to the cross-heads by pins 43 and their outer ends are each adapted to be connected to any one of a series of openings 44 in the standards 3 and 4 by the pins 45 and 46.

Inasmuch as the gear 24 is fast on the shaft 21 and inasmuch as the gear 25 with i the yoke is adapted to loat without any fixed bearing, it will be apparent that the gear 25 and the yoke will act as a counterbalance to the load carried from the cable 10 on the walking beam and it will also be apparent that by adjusting the links 40 and 41 laterally with respect to the cross-heads 34 and 35 or vertically with respect to the standards 3 and 4 or both, the throw of the walking beam can be varied and it will also be noted that the relative positions of the eccentric shafts 21 and 43 on the gears 24 and 25 can be varied by loosening the heads 26 and 27, taking the gears out oi mesh and turning the gear 25 through any arc so that through the adjustment of the links 40 or the turning of the gear 25 to vary the initial wrist pin position with respect to the shaft 21, the top of the lift can be caused to occur at 'various degrees of the cycle of rotation of the gear 24 and that when the parts are arranged as shown in any of the diagrams 4 to 9, the complementary eccentrics on the two gears will be relatively close together at the beginning of the litt or upstroke so that the ratio between the two gears at the initial up-stroke movement will be relatively low as shown in diagrams 4, 6 and 8. However, it .will be seen that the speed ration between the gears willincrease progressively during part of the cycle until the speed ratio is greatest at the limit of the up-stroke as indicated in diagrams 5, 7 and 9 and through the rest of the cycle in each instance, the speed ration between the gears will gradually decrease so that there :is a. gradually decreasing down-stroke speed and a gradually increasing lift stroke speed, This will also be true of the construction shown in Figure 3 where the piston 47 will gradually decrease its irl-stroke speed to pre vent creating a partial vacuum in the comu presser cylinder 48 but will gradually increase the out-stroke speed to torce the air through port 49.

In the diagram shown in Figure 3, the holes 50 can be arranged horizontally and vertically so that the adjustable link 49 and 41 can be horizontal and vertical or diagonal adjustment with respect to the anchoring support which corresponds to the standards 3 and 4.

In order to graphically describe the various effects resulting from the variations in adjusted positions of the links 40 and 41 and relative adjustments between the gears 24 and 25, I have shown a power curve chart in Figure 10 in which the curve X is the power curve of the arrangement shown in Figures 4 and 5. The power curve Y is the power curve of the arrangement shown in Figures 6 and 7 and Z is the power curve of the arrangement shown in Figures 8 and 9. It is thought that these three instances will amply indicate the variations that might be made although almost anyfvariations can be made that may seem desirable;

In oil wel-l practice, the yoke and gears usuallyweigh around a half a ton so they make a very effective counterbalance weight for the rods, the plunger and fluid on the up-stroke andthe rods and plunger on the down-stroke.

` arrangement of I do not wish to beilimiteid to the enact gearing illustrated lsince changes in form, proportion andminor detailsof construction may beresorted to without departing from the spirit of the invention or sacrificing any of its advantages.- What I claim and desire to `secure .by Let-V ters Patent is :-v

l. A mechanical movement comprising two meshing eccentric gears, one of which is a driving gear and the other a driven gear, a yoke in which the gears are loosely mounted, a link connected to the eccentric of the ydriven e gear and adjustable anchoring means for the opposite end ofthe link.

i 2. VA mechanical movement comprising two meshing eccentric gears, one of which is a driving gear and the other a driven gear, a yoke in which the gears are loosely mounted, a link connected to the eccentric of the driven gear and vertically adjustable anchoring means for the opposite end of the link.

3, A mechanical movement comprising two meshingeccentric gears, one of which is a driving gear and the other a driven gear, a

yoke in which the gears are loosely mounted,

a link connected to the eccentric of the drivenV gear and vertically and horizontally adjustable anchoring means for the opposite end ofthe link; ,e j i j 4. A mechanical movement comprising two meshing eccentric gears,one of which is a driving gear and the other a driven gear, a yoke in which the gears are loosely mounted, a' link connected to the eccentric o-f the driven gear,

means for adjusting the link longitudinally with respect to the gear, an anchor for the 0pposite endV of the link and means for adjustably connecting the link to the anchor.

5. A mechanical movement comprisinga drive shaft, a gear eccentrically mounted on said shaft, a yoke in which the gear is mounte the gear on the shaft, the yoke-*having a removable part whereby the second gear may be ably adjust it with respect to the first gear to change the `throw of its eccentric, an anchor and a link connected to the eccentric of the second gear and adj ustably pivoted to the anchor.

7 A mechanical movement comprising two meshing eccentric gears, one of which is a j driving gear and the other a driven gear, a VVyoke in which the gears are loosely-mounted,

a link connected tothe eccentric ofthe driven gear, adjustable anchoring'means for the op-n posite end of the link, la walking beam and i reins connecting the driven gear to the walking beam on the power endthereof, the gears and theyoke constituting a counterbalance fo-r the load carried by the walking beam.

8. A mechanical movement comprising a power shaft, a driving gearl eccentrically mountedon the power shaft, a driven eccen tric gear meshing with thedriving gear, coni tacting shrouds on the respective gears, `a yoke incasing the gears, said `yoke having grooved end bearingbars on the edges of which the shrouds roll, tie-rods connecting the bars, a link longitudinally adjustable ec-` centrically to the driven shaft, ananchor `and j j means for adjusting thelink on the anchor. Y

9. A mechanical movement Vcomprising a plurality 4ofmeshingeccentric gears, one off which is a driving gear and the'other a driven gear, a lioating means for supportingsaid ed,.a driven gear in the yoke,ineshing with moved out of mesh with the lirstgear to roj tatably adjust it with respect to the first gear to change the throw ofits eccentric, an anchor and a link Aconnected to the eccentric of the A second gear and pivoted to the anchor. Y

6. A mechanical movement comprising a 1 drive shaft, a gear eccentrically mounted on said shaft, a yoke in which the gear is mounted, a driven gear in the yoke, meshing with the gear 0n the shaft, the yoke having a removable part whereby the second gear may be 5 moved out of mesh with the first gear to rotat- 

